JPH01199100A - Regulator - Google Patents

Abstract

PURPOSE: To maintain gas consumption throughout the whole regulating area to a certain extent by providing a first spring means for pressing a high-pressure piston to the bottom of a high-pressure chamber and a second spring means for pressing a movable piston in a direction distance from a valve seat. CONSTITUTION: A cavity is separated into a first chamber 12 and a second chamber 4 by a movable piston 11. The first chamber 12 is in fluid contact with the second chamber 4 via a channel 10 and a channel 28. A high-pressure chamber 2 is disposed beneath a bottom 23 of the second chamber 4, and a high-pressure piston 1 is disposed in this high-pressure chamber 2. When the difference between a primary pressure and a pressure of chamber 4 overcomes a pre-tension of a spring 6, the high-pressure piston 1 can be displaced in a direction toward the second chamber 4. When the pressure of the chamber 12 against a working plane of the movable piston 11 overcomes a force of a second spring 17, the movable piston 11 is displaced, and the gas from the high-pressure chamber 2 is throttled.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention provides a first chamber and a second chamber separated by a movable piston that changes the dimensions of these chambers, and which chambers are in fluid contact with each other via channels and are operated under high pressure. second room
a valve seat disposed below the bottom of the chamber, a hole disposed in the bottom of the second chamber, a valve seat disposed in the second chamber for cooperation with the piston, the piston and the seat, or a sealing member and a seat cooperating with the seat; relates to a pressure regulator in which a throttle device is formed between a high pressure chamber and a second chamber.

According to the rules applicable to breathing operations with a supported gas supply, as a rule, air with a pressure of up to 300 bar, it informs the user when a given amount of breathing gas remains and is at the user's disposal. Alarm devices must be provided. This predetermined amount of gas is typically 2 times the maximum filling pressure of the gas reservoir.
Corresponds to 0%.

Such an alarm signal may be generated, for example, by a whistle that is activated automatically when the pressure in the gas supply drops to a predetermined level. Depending on the type of breathing apparatus and gas supply, and depending on the user's national regulations, the activation value of the alarm signal is between 30 and 75 bar, and in this pressure range the signal or alarm device must be activated. It won't happen. To obtain the correct breathing flow to the whistle, gas is supplied through a nozzle connected to a pressure regulator.

Such a regulator may be a specific pressure regulator connected to the first regulating stage in the breathing conduit of the device or directly from the gas source contained in a single device. It can be obtained from an i-device.

For example, the gas flow consumed to form the signal according to the CEN standard does not exceed an average of 5 liters per minute over the entire time when the pressure in the gas supply decreases from the operating value to zero. In the prior art rules, the pressure of the gas supply is consumed by the whistle, which usually increases linearly when decreasing from the operating value to zero.

One object of the present invention is to provide a dimmer that provides a constant secondary pressure over the entire range from operating pressure to substantially zero.

A second object of the invention is to devise a regulator which is adjustable within wide limits and which maintains constant gas consumption over the entire adjustment range.

Another object of the invention is to provide a regulator that provides a constant flow system over the entire range from the maximum sub-pressure of the gas supply to substantially zero.

These objects are regulators according to the preamble of claim 1, in which a high-pressure piston is arranged in a high-pressure chamber and projects through a hole into a second chamber, through which it is longitudinally displaceable; a second hole at the end of the high pressure piston faces the second chamber, a valve seat is disposed in the second hole, and the high pressure chamber is provided with fluid communication between the outside of the piston of the high pressure chamber and the second hole; A first spring means is provided for pushing the high pressure piston toward the bottom of the high pressure chamber, and a second spring means is provided for pushing the first piston away from the valve seat.
This is achieved by a pressure regulator characterized in that it is provided with spring means.

Advantageous embodiments of the invention emerge from the dependent claims.

Regarding the drawings, the regulator in FIG. 1 has an upper defining wall 25 and a hole 22.
It includes a cavity defined by a cylindrical casing 13 with a bottom 23 having a bottom 23 . Extending from the bottom 23 is a tubular member 26 that is larger than the inside diameter of the hole 22. A piston 11 is disposed within the cavity, an upper portion of the piston 11 slidably abutting the inner surface of the casing 13, and an intermediate portion of the piston 11 facing the tubular member 26.
The lower portion is spaced apart from the inner surface of member 26. The piston 11 has a cavity defined by a wall 25, an upper or first chamber 12 defined by the casing 13 and an upper defining surface 27 of the piston 11, and a bottom 23.
, a second chamber 4 defined by the tubular member 26 and the lower part of the piston 11.

The piston 11 is provided with a central channel 10 extending from its upper defining surface 27 through the upper and intermediate regions of the piston to the lower region, the channel 10 being merged with one radial channel 28, which channel IO is communicated with the second chamber 4. Therefore, the first chamber 1
2 is in fluid contact with the second chamber 4 by channel IO and channel 28. In its upper region, the piston 11 is provided with a seal 14 in sealing contact with the casing 13, and in its intermediate part with a seal 7 in sealing contact with the inner surface of the tubular member 26.

The cavity surrounded by the casing 13 is the casing 13
, bottom 23 , including a third chamber 8 defined by the outer surface of the tubular member 26 of the piston 11 . A second spring element 17 is arranged in the chamber 8 , for example a steel spring or a gas spring, and presses the piston 11 in the direction towards the upper defining wall 25 of the first chamber 12 . Chamber 8 is in fluid communication with the surrounding atmosphere by a hole 9 in casing 13.

A high pressure chamber 2 is arranged below the bottom 23 of the second chamber 4. The hyperbaric chamber 2 can be connected via a hole 29 to a source of breathing gas (not shown). A second piston l is arranged in the high pressure chamber 2, and this piston 1 passes from the bottom 23 of the chamber 2 through the hole 22 into the second chamber 4.
23 and into the second chamber itself. The outer diameter of the upper part of the piston I is such that it can be displaced along the defining wall of the hole 22. Piston l closest to bottom 24
The lower part of is designed as a collar, the cylindrical part of which is slidable along the casing 21.

The seal 5 is arranged between the bottom 23 and a washer-like member 30, which is pressed against the seal 5 with a predetermined force by a first spring member 30, for example a steel or gas spring.

At its upper end, which protrudes into the second chamber 4, the piston I is provided with an opening forming the valve seat 3 of the first piston 11, the lower region of which forms a cylindrical body with a conical tip 18. The conical tip 18 of the piston 11 cooperates with the valve seat 3 to form a throttle device 3. The bore of the piston l in the seat 3 merges with a channel 33 extending over the entire piston l. Channel 31 connects channel 33 to casing 2', 11
1, in communication with the spring housing defined by the piston l and the member 30 and the seal 5. The seal 5 has a low friction against the surface of the high-pressure piston l and separates the spring housing from the second chamber 4, so that the high-pressure piston l is connected to the pressure of the second chamber 4 by the gas cylinder pressure, hereinafter referred to as the second pressure. when the difference in pressure overcomes the pretension of the spring 6, the second chamber 4
It can be displaced in the direction toward. The channel 33 does not have to reach the lower defining surface of the piston l, but can extend downwardly in the piston communicating with the spring housing by the channel 31. Channel 3 in the piston
1 position should be such that the channel 31 is always located below the member 30 when the piston l is displaced upwards.

The first chamber 12 is provided with a capture member 34 that regulates the upward movement of the piston 11 . The capture of the upward movement of the piston l is also defined by the upper defining wall 25. The capture of the upward movement of the piston 11 is variable.

The upper defining wall 25 of the chamber 12 is, in the illustrated embodiment, the whistle 19
It is integrated with an alarm device in the form of. Above room 12 is wall 2.
A chamber 35 is separated by 5 and is in fluid communication with the first chamber 12 by a nozzle 16 . The whistle 19 is connected to the chamber 35 by a signal opening 20. Conduits to the breathing apparatus (not shown), e.g.
(ncy evacuation) or escape device whistle 1
Can be connected instead of 9.

The breathing device can then be equipped with a -constant flow of breathing gas with the aid of the nozzle 16.

With the working phase regulator, gas flows from the gas bottle into the high pressure chamber 2 through the hole 20. The gas flow then passes through channel 31 and between the chamber wall and collar 32 into the spring housing. The gas entering the second chamber 4 through the valve seat 3 increases in pressure, which is initially equal to the primary pressure, and by means of the channel 28, lO of the piston 11, the pressure increases in the first chamber 28, lO.
Propagates to O. From chamber 12, the gas enters chamber 35 through nozzle 16 and then through alarm device 19. control spring 1
7 against the capture member 34 or the wall 25 against the piston 1
1, the first piston 11 is held against the wall 24. A defining wall 25 integral with the catch 34 or alarm device 19 is inserted into the casing 13 so that the catch can be adjusted to limit the gas flow to the alarm device 19 when the primary pressure increases, as described below. Adopted to select the primary pressure when shutting off.

- engages when the next pressure decreases.

The tip 18 of the first piston 11 and the valve seat 3 form a fully open restriction in this position, but the tip 18 of the first piston 11
When the pressure in the chamber 12 against the working surface overcomes the force of the second spring 17, the tip I8 is directed towards the valve seat 3 and the first piston I
I and throttle the gas flow from the hyperbaric chamber 2.

Adjustment phase l First piston 11 with spring 17 and throttle valve 3.18
limits the pressure in the second chamber 4 and the first chamber 12 to a level determined by the equilibrium between the force of the spring 17 and the primary pressure on the tip 18 and by the pressure on the working surface of the first piston 11. Acts as a pressure regulator.

Since the force on the tip 18 increases as the primary pressure increases, the secondary pressure P2 in the chamber 12 is not necessarily constant, but is subject to an additional force dP2·k x dPl.

Here k is the pressure absorption area of the tip 18 and the first piston 1.
This is the relationship with work surface 1. As long as the pressure difference PI - P2 cannot overcome the tension of the spring member 6, the high-pressure piston l rests against the bottom 24 of the high-pressure chamber 2.

Adjustment Phase 2 When the pressure PI increases to such an extent that the pressure difference PI-P2 overcomes the tension of the spring 6, the second piston l and the first piston 11 begin to be displaced in the direction towards the capture device 34. The tip 18 is only affected by the pressure difference PI-P2 and therefore does not come into contact with the valve seat 3.

- When the pressure increases further, the piston 1111 is affected by the magnitude of the pressure increase, the working area of the second piston l (this is the difference between the area of the hole 22 and the spring constant of the spring member of the valve seat 3) and the spring member The displacement is proportional to the pressure increase by a distance determined by the spring constant of 6.

In this case, the pressure regulator is functioning as described in "Regulator I", but the tension of the second spring is increased by the same distance that the pistons', 111, 11 have moved, and The difference is that the force of the second spring 17 on the first piston 11 decreases in proportion to the increase in primary pressure. However, this pressure reduction is offset by the fact that the first piston 11 is subjected to an additional force in that the same primary pressure increase acts on the pressure area of the tip 18.

In the regulator of this embodiment, the pressure area of the valve seat 3 is adapted to the area and spring constant of the piston, and the reduction in the force of the regulating spring 17 is completely offset by the additional force. As a result, the pressure regulator has a constant secondary pressure and the nozzle 16 has a flow as a function of the primary pressure in the regulator 2.

By over- or under-compensating the decrease in the force of the secondary spring I7, it is possible to achieve an increasing or decreasing secondary pressure characteristic.

De-energizing and energizingAs mentioned above, as soon as the preload force of the spring 6 is overcome by the secondary piston l at a low primary pressure, the pistons', 11
1 and 11 are displaced by a distance proportional to the increase in primary pressure. When the primary pressure increases to such an extent that the pistons', 111, and 11 are displaced until the first piston 11 comes into contact with the catching part 34, the positions of the first piston 11 and the tip 18 are fixed, and - If the pressure continues to increase, the valve seat 3 of the second piston l will be pressed against the tip 18, in which case the gas flow to the alarm device 19 will be cut off.

Since the second chamber 4 is depressurized, the pressure difference across the high-pressure piston 1 is amplified, resulting in a shut-off. - The contact pressure of the throttling device 3.18 increases significantly as the secondary pressure increases to its final level, which is typically a maximum of 300 bar.

When the contents of the gas bottle are consumed and the pressure decreases and the contact pressure becomes zero again, the second chamber 4 is under pressure and, conversely,
The throttle valve 3.18 opens, the pressure regulator then starts operating in the regulator 2 and the gas flow is again supplied to the alarm device 19. When the remainder of the contents of the gas bottle is consumed, the secondary pressure remains almost constant during the period of the regulator 2, so the alarm device 19 sounds at full power until the secondary pressure equals the primary pressure, and then The power of the signal decreases until it comes to a complete stop.

Since deenergization occurs when the second chamber 4 is under pressure and energization occurs when the second chamber 4 is under pressure, i.e. at a different pressure difference of the high-pressure piston l, energization occurs at a lower primary pressure than deactivation. do. This difference is at least equal to the secondary pressure, for example 7 bar. In practice, this difference is approximately 15 bar, since frictional forces act in opposite directions during de-energization and energization.

Adjustment of the regulator is performed with respect to bias. Dimensionally, the spring constant and the pretension of the spring 6 are determined first, so that the high-pressure piston 1 is forced to e.g. 80 bar and 2 bar respectively.
Between the maximum and minimum biasing pressure of 0 pearls, adjustment provides an acceptable stroke length, for example 2.5 am. The remaining dimensions are then calculated.

When the regulator of the present invention is employed as a constant flow device in a breathing apparatus, such as an emergency evacuation device with a constant flow of breathing gas,
The catch 34 is arranged in a widely spaced relationship from the first piston 11 so that even if a maximum-order pressure acts on the high-pressure piston 1, the piston 11 does not come into contact with the catch 34. The spring constant of the spring and the working surface of the regulator piston are dimensioned similarly to the nozzle 16, so that when the secondary pressure in the chamber 12 (at a given primary pressure) reaches a predetermined level, the nozzle 1
6 to obtain a predetermined constant flow.

The regulator then operates according to regulator 2 from this given level up to the maximum operating pressure and vice versa. When the throttle device 3.18 of the inventive regulator is closed with a high primary pressure, the secondary pressure is zero. - When the secondary pressure reaches a predetermined level, the throttling device is opened', 111, a secondary pressure is obtained in the chamber 12, which is constant with respect to the decreasing primary pressure and is delivered through the nozzle 16; The gas amount is constant and can be selected, for example, up to 5 liters per minute.

A modification of the regulator of FIG. 1 is shown in FIG.

It lacks piston 11, channel 10.28. The first chamber 12 in this example has a channel 110 provided through the wall 13 and extending to the bottom 23 of the second chamber 4 between the first hole 22 and the bottom of the tubular bag M26. Channel 33° of the high pressure piston does not pass through the entire piston in this embodiment. High pressure gas passing through hole 29 passes through collar 32, similar to the embodiment of FIG.

Another embodiment of the regulator of the present invention is shown in FIG.

According to this embodiment, the piston 11 is replaced by a piston 111 whose upper section is directed towards the upper definition of the first chamber. This upper section has a smaller diameter than the corresponding part of the piston 11. The piston 111 does not abut the housing 113, but is movably connected to the housing 113 via a membrane 150 which is fixedly tensioned in the upper region of the piston 111 and on the wall 113. Also in this case, a first chamber 112 is provided which is separate from chamber 4 but in fluid contact with chamber 4 via channel 1O128.

The piston 111 differs from the piston 11 of FIG. 1 in that its end facing towards the high pressure chamber 102 is flat. A sealing element 39 is arranged between and which cooperates with the valve seat.Such a sealing element 39 can also be provided in the regulator of FIG. The end of 11 is flat or the end of the piston has a shape corresponding to the upwardly facing side of the sealing element shown.

The upper defining wall of the chamber 112 presents a fixed annular outer part 151 and a central inner part 125, the distance of which from the area facing the chamber 112 is adjustable with respect to the corresponding area of the outer part 151. Since the upper section of the piston 111 has a smaller diameter than the central inner portion 125 of the upper defining wall of the chamber 112, the piston 111
1 can abut the inner part 125 or a specially provided catch 134. In the former case, portion 125 is the first
It constitutes a trap 134 for the upward movement of the piston.

The lower part of the regulator according to FIG. 3 has also been modified, piston 1 being replaced by piston 111 and piston 111
has a collar 132 in its lower region that is smaller than the high-pressure piston l. Furthermore, the lower section of the piston 101 is connected to the wall 121 via a membrane 152. Inlet hole 129 empties into the lower area of cavity 102 below membrane 152 .

The piston lO1 is provided with a channel 133, which runs along the entire length of the piston 10117) from the end facing towards the chamber 4, but instead of being a through channel, it pours into the side wall of the piston 101 below the membrane 152. You can also do that.

In the first hole 122 of the bottom 123, a guide ridge (not shown)' of the piston 101 is provided, which allows the gas from the chamber 4 to flow through the piston 1', 101, the membrane 152 and the wall 12! and flows into the space defined below the bottom 123. channel 1
53 can connect this space to the second chamber 4.

The regulator according to FIG. 3 operates in a similar manner as the regulator according to FIG. The membrane 152 on the wall 121 and the piston lO1 and the manner of tensioning suitable membranes for this purpose are well known to those skilled in the art.

Of course, the seal 7 between the first piston 111 and the inner surface of the tubular member 26 can be replaced by a membrane as described with respect to FIG.

FIG. 4 shows an embodiment of the regulator according to the invention, which operates according to the countercurrent principle. The regulator includes a chamber 170 defined at the top by a top wall 171 having a hole 172 therein. By such means, chamber 170 is placed in communication with the surrounding atmosphere. The upper part of the first piston 211 is movable along the side wall 213 of the chamber 170.

The upper portion of piston 211 abuts a seal 214 that seals against wall 213 . The spring member 176 is connected to the piston 21
1 and the wall 171, the spring member presses downward in the figure. The first member 212 includes a hole 216 in the side wall 213 with an outlet connected thereto.

The bottom of the chamber 170 has a central hole 2 corresponding to the inner surface of the tubular member 26.
26, and a peripheral hole 173 connecting the first chamber 212 to the second chamber 204. The bottom 223 of the second chamber 204 is connected to a central hole 222 shown on the right side of FIG. 4 through which the high pressure piston 201 extends.
2 is shown. According to the left part of FIG.
It can accommodate 23 full surfaces. The high pressure piston 201 has a hole 22
The high-pressure piston 201, which is displaceable along a plane 2 and sealingly faces this plane via a seal 205, is provided with a through channel 233 having a smaller diameter at the top than at the bottom.

The lower end of piston 211 is displaceable through channel 233. Channel 233 in piston 201
The transition between the narrow and wide portions of the valve seat 203 forms the valve seat 203 .

In the second chamber 204 , a spring member 217 maintains the high pressure piston 201 in a spaced relationship from the upper defining wall of the chamber 204 .

A sealing element 239 is arranged in the channel 233 of the piston 201 . Element 239 is held loosely against valve seat 203 by spring means 175.

A hole 229 is provided at the bottom of the high pressure chamber 202 for gas from a high pressure source.

With the various parts of the regulator in the positions shown, as the pressure in high pressure chamber 202 increases, piston 201 is displaced upwardly. As a result, the throttle member (203: 239) is opened and the gas flows into the first chamber 204 through the channel 173 and into the first chamber 21.
2. Since the upper area of the piston 211 facing towards the chamber 212 has a large area, the first piston 211 is displaced upwards and the spring member 176 applies a counterforce to the piston 21.
Occurs for 1. The piston 211 is the piston 201
is displaced upwards by a distance slightly greater than the distance previously moved, so that the sealing element 239 abuts the seat 203 and blocks the flow of gas from the high pressure chamber 202 into the second chamber 204 . As gas is removed from the first chamber 212, its pressure decreases;
In that case, the piston 212 is displaced downward, and the piston 211
The lower area of the seat 239 displaces the sealing element 239 downwards.
Remove from contact with.

Of course, the regulator of the invention shown in FIGS. 1 and 2 can be modified, for example, so that the second chamber 4 is U-shaped or L-shaped. In such a case, the bottom of the chamber 4 is directed upwards instead of downwards and can be articulated at three or two points. Of course, it is also conceivable to combine the embodiments of the invention shown in FIGS. 1-3 by various means.

All spring means 6.17.175.176.217 are preferably linear over the entire working range, i.e. Hooke's law F
= The spring constant k at km is constant.

In this equation, F is the force exerted by the spring at linear distance X. In some applications, non-linear springs can be used.

The invention is not limited to what has been described and illustrated, but may be modified without departing from the scope of the invention and the claims.
Possible changes are possible.

[Brief explanation of the drawing]

1 is a cross-sectional view of one preferred embodiment of the regulator of the present invention, FIG. 2 is a cross-sectional view of a modified embodiment of the regulator of FIG. 1, and FIG. 3 is a cross-sectional view of another preferred embodiment of the regulator of the present invention. FIG. 4 is a cross-sectional view of another embodiment of the present invention. 12, +12.212. ,,first chamber, 4.204.
, , 2nd room, 1111F, Ill, 211, ,
, piston, 2.102. ,,hyperbaric chamber,1,bi,lot,2',101,. ．． High pressure piston, 6.21
7. ,,spring means, 17.176,. Second spring means. Patent Applicant Intelspiro Activolag

Claims (1)

[Claims] 1. The first chamber (12, 112, 212) and the second chamber (4
, 204), but these chambers (12, 112, 212; 4
, 204), the movable pistons (11, 11)
', 111, 211) and these chambers are in fluid contact with each other via channels (10, 110, 173), connecting the high pressure chamber (2, 102) to the second chamber (4, 20
4), the holes (22, 122, 222) are placed under the bottom (23, 123, 223) of the second chamber (4, 204), and the valve seat is placed under the bottom of the second chamber (4, 204).
4, 204) and pistons (11, 11', 11
1, 211), and the pistons (11, 11', 1
11, 211) and seat or sealing element (39, 239)
The tortoise (3, 203) is connected to the hyperbaric chamber (2, 102) and the second chamber (
4, 204), the high pressure piston (1, 1', 101, 201) is connected to the high pressure chamber (
2, 102) and the first hole (22, 122, 222).
) into the second chamber (4, 204)), and through this hole can be longitudinally displaced, the second
The hole faces the second chamber (4, 204), the valve seat (3, 203) is placed in this second hole, and the gap between the outside of the piston in the high pressure chamber (2, 102) and the second hole is Fluid connection (33, 3
1; 33';133; 233) to the high pressure piston (1, 1
', 101, 201), and the high pressure piston (1, 1', 101, 201) is installed in the high pressure chamber (
2, 102) toward the bottom of the first spring member (6, 2);
17), and the first piston (11, 11', 111) is connected to the valve seat (3, 2
A second spring member (17) that presses away from the second spring member (17)
, 176). 2. Regulator according to claim 1, characterized in that the spring constant of the first spring member (6, 217) is constant over the entire operating range of the spring. 3. Adjuster according to claim 1 or 2, characterized in that the spring constant of the second spring member (17) is constant over the entire operating range of the spring. 4. The first chamber (12, 112, 212) is connected to the valve seat (
3, 203) in the direction away from the first piston (1
1, 11', 111, 211)
34, 134), whereby said first piston (1
1, 11', 111) are high pressure pistons (1, 1', 1
01, 201) is in the closed position and Regulator according to one or more of the preceding claims, characterized in that it is moved into an open position. 5. The catching part (34, 134) is adjustable to be at various intervals from the upper defining surface of the first piston (11, 11', 111) when placed at the lowest position. The regulator according to claim 4. 6. The upper defining wall of the first chamber (12, 112, 212) has nozzles (16, 21) in fluid communication with the alarm device (19).
6) The regulator according to claim 4 or 5, characterized in that the regulator comprises: 6). 7. The first chamber (12, 112, 212) is connected to the valve seat (
3, 203) for the displacement in the direction away from the trap (
34, 134), the catching portion is spaced apart from the upper defining surface of the first piston (11, 11', 111), and the maximum pressure of the high pressure chamber (2, 102) is equal to the maximum pressure of the high pressure chamber (2, 102). Regulator according to one or more of the preceding claims, characterized in that the high-pressure piston (1, 1', 101) cannot be displaced to such a distance that the first piston reaches the catch. 8. The upper defining wall (25,
8. Regulator according to claim 7, characterized in that the nozzle (16, 172) communicates with a device driven with constant flow. 9. The trapping section (34, 134) is connected to the first chamber (12,
9. Regulator according to one or more of claims 4 to 8, characterized in that the upper defining wall (25, 125) of the upper defining wall (112). 10, the seat (3, 203) and the first piston (11
, 11', 111) is formed in cooperation with the high-pressure piston (1, 1', 101, 201).
, i.e. the first hole (22,
122, 222) and the sealing area of the diaphragm, and each spring member (6; 175, 217; 17, 1
76), and displays the spring constant of the first chamber (12, 212).
) is approximately constant within a certain range regardless of pressure fluctuations in the high pressure chamber (2, 102), and in this range, the pressure in the high pressure chamber (2, 102) is equal to the pressure in the second chamber (4, 204). )
The high pressure pistons (1, 1', 101,
201), and finally the first piston (1, 1
Regulator according to any one or more of claims 4 to 9, characterized in that the first chamber (12, 102) is in contact with the capture part (34, 134, 171) of the first chamber (12, 102). . 11. The pressure in the first chamber (12, 212) is equal to the pressure in the high pressure chamber (2
, 102). 12. The pressure in the first chamber (12, 212) is equal to the pressure in the high pressure chamber (2
, 102). 13, the first piston (111) has a casing (11
3) A membrane (1) stretched inside and inside the piston (111).
50) and/or a high pressure piston (101
) comprises a membrane (152) stretched within the casing and within the piston (101).
2. The regulator according to any one or more of 2.